Fluid pressure energy translating device



Feb. 9, 1960 v. v. BLASUTTA ETAL 2,924,182

FLUID PRESSURE ENERGY TRANSLATING DEVICE Filed Aug. 31, 1955 v 20 3 Sheets-Sheet 1 so 69 22 45 4 "5e.

29 u i 39/ 4| 3 4o 67 s2 s3 J 68 Fig- E mmvrox. VICTOR v. BLASUTTA I 24 JOHN F. HEDGE BY .z fi

'Fi g AGENT Feb. 9, 1960 Filed Aug. 31, 1955 V. V. BLASUTTA ET AL FLUID PRESSURE ENERGY TRANSLATING DEVICE 3 Sheets-Sheet 2 N TOR.

INVE VICTOR BLASUTTA JOHN F. HEDGE v. v. BLASUTTA ETAL 2,924,182

FLUID PRESSURE ENERGY TRANSLATING DEVICE Feb. 9, 1960 3 Sheets-Sheet 3 Filed Aug. 31, 1955 INVENTOR. VICTOR V. BLASUTTA JOHN F. HEDGE United States Patent Oflice 2,924,182 Patented Feb. 9, 1960 FLUID PRESSURE ENERGY TRANSLATING nEvrcE Victor V. Blasutta, Columbus, and John F. Hedge, Worthington, Uhio, assignors, by mesne assignments, to American Brake Shoe Company, New York, N.Y., a corporation of Delaware Application August 31, 1955, Serial No. 531,807

2 Claims. (Cl. 103-136) This invention relates to fluid pressure energy translating devices such, for example, as hydraulic pumps or motors.

The invention is described and illustrated herein in connection with a rotary type hydraulic pump or motor of the capsule type. For the sake of brevity the invention is described hereinafter as being applied to a fluid pressure energy translating device in the form of a pump but it is to be understood that the invention is not to be limited by such description to a pump.

An object of this invention is to provide improved and simplified structure in a pump.

Another object of the invention is to provide an improved pump apparatus which includes improved and simplified means for conducting fluid within the apparatus.

Another object of the invention is to provide improved and simplified construction in a capsule type pump i.e., a pump in which pump elements are inserted in a housing or casing and which housing or casing includes passage means for conducting fluid to and from the pump.

Another object of the invention is to provide improved structure in a pump of the type set forth in the foregoing object in which the pump includes improved means by which the high pressure fluid passages in the pump are formed and connected with the high pressure fluid passage means in the casing or housing and preferably, but not necessarily, wherein certain of the pump elements are held together by fluid pressure taken from said passages.

In carrying out the foregoing object, it is another object of the invention to cause a cheek plate of the pump, which may or may not function as a piston in the housing, to include all of the high pressure fluid passages of the pump and to connect the pump directly with the high pressure fluid passage means in the housing.

Still another object of the invention is to cause the cheek plate set forth in the foregoing object to coper ate with walls of the casing or housing to provide a pressure chamber and to provide a restricted passageway for conducting fluid pressure existing in the high pressure passages to said chamber whereby said cheek plate will function as a piston to urge pump elements within the casing or housing together in an axial direction.

Still another object of the invention is to provide an improved pump of the type set forth having a housing including two elements in each of which there is an' inlet or outlet passage and wherein said casing or housing elements may be rotated with respect to each other to change the relative positions of said inlet or outlet passages, the internal arrangement of the pump being such that said passages are in communication withpassages of the pump regardless of the relative positions occupied by the casing or housing elements.

Yet another object of the invention is to provide an improved cheek plate for use in a pump of the type described.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the. accompanying drawings wherein a preferred form of embodiment of the invention is clearly shown.

In the drawings:

Figs. 1 and 2 are views in section of an improved capsule type pump or motor including features of the invention, Fig. 2 being a view taken on line 22 of Fig. 1, looking in the direction of the arrows;

Fig. 3 is a view looking at the left-hand end of the pump seen in Figs. 1 and 2 after a cover or cap and cheek plate thereof have been removed, the view showing construction and arrangement of the cam ring, rotors and vanes, etc. of the pump;

Fig. 4 is a view similar to Fig. 3, but showing the cam ring rotated in a clockwise direction with respect to Fig. 3 to permit operation of the apparatus in .a direction reversed from that of Fig. 3;

Fig. 5 is a view in elevation of the port side of a check plate employed in the pump, and

Figs, 6 and 7 are views in section, the views being taken on lines 6-6 and 77, respectively, of Fig. 5.

Thepump shown in the drawings is of the capsule type, that is, it includes a casing or housing 20 having a cylindrical wall 21 and end wall 22 which walls cooperate to form a hollow cylindrical chamber 23 in which a rotary vane type pump 24 is contained. The casing 01' housing 20 also includes a boss 25 which extends radially from its cylindrical wall 21 and forms a high pressure fluid outlet or exhaust passage 26 which leads radially through the wall 21 and terminates at its itnerior cylindrical surface in opening or port 27. A readily removable internally threaded hollow flange 28 is secured by bolts, not shown, to the outer end of boss 25. Flange 28 is provided for the purpose of permitting quick and easy connection and disconnection of the pump casing or housing 20 to the high pressure side of a hydraulic system, not shown.

The end of chamber 23 opposite the end wall 22 is closed by a cap or cover 29 secured to one end of the cylindrical wall 21 by a plurality of screws 30 and this cap or cover 29 includes a radially extending boss 31 which forms a low pressure fluid inlet, conduit or passage 32 extending from its cup shapedinterior to its exterior, and of course, from the outside to the inside of easing or housing 20 for admitting fluid into the housing. A flange 33 similar to flange 28 is secured to boss 31 for connection and disconnection of the pump housing or casing 20 from the low pressure side of said hydraulic system.

It may be mentioned here that one of the advantages of the pump is the fact that its cap or cover 29 may be secured to the casing or housing wall 21 in different rotated positions to change the radial relation of the inlet andoutlet passages 32 and 26 thereby to render the pump more versatile to connection with the low and high pressure sides of said hydraulic system.

The pump assembly 24 includes a pair of rigid cylindrical check or port plates 34 and 35 between which a cam ring 36 is sandwiched. These elements 34, 35 and 36 telescope Within the cylindrical chamber 23 and are interlocked against relative rotation with respect to each other and the cap or cover 29 of easing or housing 20 by a pin 37 which extends through aligned openings in the cheek plate 34 and the cam ring 36 and into sockets in the cap or cover 29 and cheek plate 35, as shown in Fig. 2 of the drawings.

The cheek plates 34 and 35 and the cam ring 36 cooperate to provide a rotor chamber in which there is a rotor assembly 38 including a rotor body provided with radially extending circumferentially spaced vane slots in each of and ports 48 into the rotor chamber.

which there is a vane 39. Vanes 39 are urged radially outwardly by springs 40 seated in sockets formed in the rotor body at the bottom: of each of said vane slots. Pump 24 also includes a shaft 41 which extends into the casing or housing 20 through a central bore in the end wall 22 thereof and'through the cheek plate 35, the rotor body and into the cheek plate 34. Shaft 41 is mounted ad acent 1ts exposed end in a ball bearing 42 in said central. bore in end wall 22 and its opposite end is mounted in. a roller bearing 43 carried in a central through bore in the cheek plate 34.

Because the cheek plates 34 and 35 and the cam ring 36 are telescoped with a close fit into the. chamber 23 and float axially therein, it is necessary to provide for relative movement between the shaft and the cheek plate 34 as well as the rotor body and the shaft. For this reason, and to permit expansion and contraction of the elements of the apparatus, the construction at the .roller bearing 43 is such that some relative axial motion between the cheek plate 34 and shaft 41 may occur and the roller bearing is connected to the shaft 41 through a motion permitting spline connection 44. Axial movement of shaft 41 is prevented by the ball bearing 42. Ball bearmg 42 is secured in the central bore in end wall 22 and against an annular seal ring or plate 45 by a pair of snap rings.

The cheek plate 34 is provided with an annular'shoulder 46 on its side adjacent the cap or cover 29 and this i two diametrically positioned fluid inlet, suction or low pressure passages 47 which lead therethrough from the chamber, said passages 47 terminating inelongated inlet also struckfrom the axial center of the rotor chamber. All four of the arcuate portions 53 and 54 of the peripheral wall of the rotor chamber are interconnected by.

ramps, the intake, suction or low pressure ports 48 being positioned at diametrically positioned ramps 55 and high pressure, outlet or exhaust ports 5 56 formed in the cheek plate 35 being disposedadjacent diametrically disposed ramps 57. g

As indicated in Fig. 3 by an arrow formed in the cam ring 36 and positioned adjacent the pin 37, the rotor assembly 38 will be rotated in a clockwise direction. The inlet ports 48, 52 and ramps 55 are each located at the end of one of the sealing sections 53 and in advance of one of the transfer sections 54 while one of the exhaustports 56 is located at each of the ramps 57 at the end of each transfer section 54 and in advance of the nextadjacent sealing section 53. As is well understood in the art, when the rotor assembly38 is. rotated in the direction of the mentioned arrow, the vanes 39 will cause fluid to be transferred from the inlet ports 48, 52 across .thetransfer sections 54 and to. be-expelled through the exhaust ports In Fig. 4 of the drawings, the cam ring 36 is shown in a position rotated 90 in a clockwise direction from that of Fig. 3 to reverse the direction of rotation of the rotor assembly 38 and shaft 41. In this position, the ramps 57 are aligned with ports 48, 52 and ramps 55 are aligned with ports 56.

The cam ring 36 may be rotated from the position shown in Fig.3 to the position shown in Fig. 4 without removing it from. the rotor assembly 38. To rotate the cam ring 36. the cap or cover 29 is removed from the cylindrical wall 21 of easing or housing 20 to expose the cheek plate 34. Check plate 34 is then withdrawn from the casing or housing 20 to expose one end of both the j cam, ring 36 and the rotor assembly 38 and, upon reports 48 formed by the face or wall of the cheek plate 34 immediately adjacent the rotor assembly 38.

As clearly shown in Fig. 1 of the drawings, the cheek plate 34 includes a pair of passages 49 which connect the inlet, suction or low pressure passages 47 with elongated ports 50 which register with the inner ends of the vane slots in the rotor body as the slots rotate past the ports 50.

From the foregoing, it will be apparent that the path of fluid to the rotor chamber of the pump 24 is through the flange 33 and passage 32 to the large reservoir-like interior of cap or cover 29 and through the passages 47 apparent that fluid will be admitted to the inner and outer ends of the vanes 39 each time the vanes 39 and their slots in the rotor body pass the ports 48 and 50.

Cam ring 36 includes a plurality of axially extending through bores 51 which conduct fluid from the inlet ports 48 to ports and passages 52 formed in the face of cheek plate 35 which is adjacent the cam ring 36. These ports and passages 52 duplicate the passages 47 and 49 and It will also be 1 the ports 48 and 50 on the opposite side of the rotor chamber.

Because of the above described arrangement of the elliptical shape and it includes two diametrically disposed sealing portions 53 of equal radii struck from the axial center of the rotor chamber which, of course, is the axis of shaft 41, and two diametrically disposed transfer portions 54 of equal but larger radii than the sealing portions 53. The radii of the transfer portions 54 at 'rnovalof the pin 37, the cam ring 36 may be rotated until an. opening 58 therein becomes aligned with the .pin socket in thecheek plate 35 whereupon the apparatus may be assembled in an order reverse to that described.

A second arrow formed in the cam ring 36 adjacent the opening 58 in which the pin 37 is positioned upon rotation ofthe cam ring 36 indicates'the new direction of rotation of the rotor assembly 38. It is to be understood that if the apparatus is to function as a motor, rather features of this invention and the structure of this check plate will best be understood with reference to Figs. 5,6 and 7 of the drawings. The cheek plate is a very rigid circular disk which is preferably, but not necessarily,

formed by casting and it floats within the chamber 23 in an axial direction only, its diameterbeing such as to provide a very close fit with the. interior of the cylindrical wall 21 of the casing or housing 20. As'previously mentioned, the cheek plate 35 includes in its end surface which abuts the cam ring 36 (Fig. 5) the two inlet port passages 52 and the two outlet ports 56. These passages 52 and ports 56 are spaced apart and the ports 56 are connected through cored passages 59 in the cheek plate with a relatively large endless groove 60 formed in the periphery of and encircling the cheek plate 35. Passages 59 are bifurcated as at 61 and are connected with ports 62 formed in said end surface of the cheek plate.-

ports 50 in cheek ameter of which is also such as to provide a very close 1 butslidable sealing .fit with the interior of theicylindrical wall 21 of casing or housing v20. Aspseen in Figs; 1 and .6, the flange 65 includes a small diameter bore or resistor passage 66 whichextends through the flange from the groove 60 to the adjacent end of the cheek plate 35. The function of this bore or resistor passage 66 will also be set forth hereinafter. 7

Referring again to Figs. 1 and .2 of the drawings, the cheek or face plate 35 is positioned within the chamber 23 formed by the cylindrical and end walls 21 and 22, respectively, of the casing or housing 20 and between the cam ring 36 in said end wall 22 with its annular collar 64 telescoped into the central bore in end wall 22. A suitable O-ring seal seals the collar 64 with said bore and a suitable shaft seal 67 contained within .the central bore 53 of check plate 35 seals the shaft 41 with the seal ring 45, the latter being sealed with the bore in end wall 22 by an O-ring. Cheek plate 35 functions as a piston and is urged away from the end wall .22 and against the cam ring 36 by coil spring 68 which surrounds the shaft seal 67 and engages the cheek plate :35 and seal plate 45 at its opposite ends. An O-ring iseal contained in a groove in the cylindrical wall 21 of housing 29 surrounds the cheek plate 35 to prevent any loss of hydraulic fluid under discharge pressure from the groove 60 between the cylindrical wall 21 and the cheek plate 35.

It is to be particularly noted that the high pressure outlet opening 27 in the cylindrical wall 22 of housing 20 is aligned with or is in register with the peripheral groove 60 in the cheek or face plate 35 when the pump is assembled and that the path of fluid being discharged from the pump under high pressure is from the outlet ports 56 through the passages 59 to the peripheral groove '60 in cheek plate 35 and in circumferential directions .in said groove 60 which cooperates with the cylindrical wall 21 to form a circular conduit or passage leading to the port 27 and through the port 27 to thehigh pressure outlet passage 26.

It is also to be noted that the end ofthe cheek plate '35 opposite the cam ring 36 and adjacent the casing or housing end wall 22 is spaced from the latter to provide an annular pressure chamber 69 within the casing or housing 20 and that the small diameter bore, orifice or resistor passage 66 in flange 65 of cheek plate 35 connects the groove 60 with this chamber. The bore or resistor passage 66 conducts high pressure from the groove 60 to the annular pressure chamber 69 and the pressure in this chamber aids the spring 68 in urging the cheek plate 35 against the cam ring 36. It is also important to note that there is substantially no flow of liquid from the pump through the chamber 69 to the high pressure outlet passage 26 and that pressure is transmitted to the chamber 69 from the groove 60 through the resistor passage 66. Resistor passage 66 functions as a choke to impede sudden changes in pressure in the chamber 69 thereby to minimize axial fluttering of the cheek plate in the casing or housing 20 due to sudden fluctuations of pressure in the outlet passage 26.

It will be seen that usually pressure in the chamber 69 will be equal to the discharge pressure of the pump and that therefore the pressure urging the cheek plate 35 toward the cam ring 36, the cam ring 36 toward the cheek plate 3 and the cheek plate 34 toward the cap or cover 29 will be proportionate to the output pressure of the apparatus.

In pumps of the type shown and described herein, there is a slight leakage of fluid under high pressure between the cam ring 36 and the cheek plates 34 and 35 and this fluid flows to between them and the cylindrical wall 21. This fluid, of course, finds its way between these elements and to the seals such as the O-ring seal, indicated at 70, between the cap or cover 29 and the gylindrical wall 21 of easing or housing 20 and its loss from the casing or housing 20 is prevented by such seal. Hydraulic pressureat the Q-ring sea l ,70, would act to separate" the cap29 from the. cylindrical wall 21 and,- of course, apply additional loads ,upon the screws ,30 which hold the cap, .29 and ,wall- 21 together. For obvious reasons, such :acondition is. to be avoided and it is avoided in the pumpsshown in the drawings.

The pressure of the fluid leaking from the rotor cham: ber between the cam ring 36 and cheek plates 34 and 35 toward the cylinder wall- 21 acts' to balance the force exerted on the cheek plate 35hy pressure in the chamber 69 and thereby tends to separate the cam ring and cheek plates. In the pump shown in the drawings, this action is reduced to a minimum. Provision has been made in the apparatus shown in the drawings for returning fluid which leaks or is forced to between the cylindrical wall 21 and the cheek plates andcam ring to the low pressure or suction ports of the pump. These provisions include the forming of peripheral chamfers 71 .(see Figs. 5-7) on the edges of surfaces ,of the cheek plates 34 and 35 which abut the cam ring 36 aswell as similar chamfers on the ends of the cam ring. As clearly shown in Figs. 1, 5 and 6 of the drawings, the chamfers 71 are connected with the inlet, suction or low pressure passages in the cheek plates 34 and 35 :by radially extending grooves or slots 72 formed in the cheek plates 34 and 35.

Because the grooves formed by the chamfers 71 at the peripheries of the cam ring and cheek plate are connected with the inlet, suction-orlow pressure passages in the cheek plates 34 and 35 by the grooves or slots 72, the pressure in said grooves" will be substantially equal to the pressure in the inlet, suction .or'low pressure passages. It will thus be seen that the pressure of the fluid which leaks from the rotor chamber between the cam ring 36 and cheek plates 34 and 35 toward the cylindrical wall 21' will be reduced to inlet or suction pressure at the grooves: formed bythe chamfers 71 and hydraulic pressure between the cylindrical wall 21 and the cam ring 36 and face platesz34' and 35 will at all times b'e-substantially equal; to theinlet or suction pressure existing in the passages 47: y

' It will also be seerrthat since; hydraulicpressure cannot build up between the cylindrical wall 21 and the peripheral sides of the cam ring and face plates that there can be no build up of pressure between the face plates and cam ring and, therefore, that counterbalancing by such pressure of the pressure in the chamber 69 will be minimized.

By this invention, there has been provided an improved fluid pressure energy translating device which is of more simple overall construction and one in which each of the elements is simplified so as to minimize the cost of manufacture and, therefore, the cost of manufacture of the entire apparatus. The construction of the apparatus is such that its parts need only to be fitted into the casing or housing and when so fitted automatically align with each other andwith the inlet and outlet passages of the casing or housing. For these reasons, the apparatus is well adapted for mass production thereby further reducing the cost of manufacture of the apparatus.

The apparatus is also more versatile to connection in a hydraulic system since its cap or cover 29 including the low pressure passage 32 and the cheek plates 34 and 35 together with the cam ring 36 attached thereto may be rotated as a unit to different positions with respect to the casing or housing wall 21 and high pressure passage 26. This is made possible because the port 27 will be aligned with the groove 60 regardless of the relative rotated positions of the inlet and outlet passages 32 and 36, respectively.

While the form of embodiment of the present invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.

We claim: a i i 1. Hydraulic apparatus'having housing'means forming a cylindrical chamber and including a cylindrical wall, an end wall and a cap closing itsother end, said cylindrical wall having'means forming ahigh pressure passage leading radially therethrough and saidcap hav-.

ing means forming a low pressure passage leading radially therethrough, means for attaching said cap to said cylindrical wall whereby the cap may be secured thereto indifierently rotated positions; a rotary'vane type fluid pressure energy translating device in said chamber including means forming a pair of check plates; a cam. ring between said cheek plates, saidcheek plates and cam ring cooperating to provide a rotor chamber; a rotor in said chamber; one of said cheek plates abutting said cap and including means forming a pair of diametrically positioned low pressure passages extending between said low pressure passage in said cap and said rotor chamber, the other of said check plates functioning as a piston in said chamber and including means forming a peripheral groove therein cooperating with said cylindrical wall of said chamber to provide a high pressure'passagc; said high pressure passage in said cylindrical housing wall registering with said peripheral groove; means forming a pair of diametrically positioned passages in :said last named cheek plate extending between said rotor chamber and said groove, and means forming a restrictor passage between said groove and the side of said last mentioned cheek plate opposite said cam ring, said check.

plate and housing walls cooperating to provide a pressure chamber, said restrictor passage interconnecting said pressure chamber and said groove whereby pressure in said chamber will urge said last named face plate against said cam ring and said cam ring against said other face plate.

2. Hydraulic apparatus having housing means forming a cylindrical chamber and including a cylindrical wall, an end wall and a cap closing its other end, said cylindrical wall having means forming a high pressure passage leading radially therethrough said cap having means forming a low pressurelpassage leading radially there- 1 through; a rotary vane type fluid pressure energy translating device in" said chamber including means forming a pair of cheek plates; a cam ring between said check plates, said check plates and cam ring cooperating to provide a rotor chamber; arotor in said chamber; one of said check plates abutting said cap and including means forming a low pressure passage extending, between said ber, the other of said check plates functioning asa piston in said chamberand including means forming a peripheral groove thereincooperating with said cylindrical wall of said chamber to provide a high pressure passage; said pressure passage in said cylindrical housing wall registering with said peripheral groove; means forming a passage in said last named cheek plate extending between said rotor chamberand said groove,and means forming a restrictor passage between said groove and the side of said lastmentioned cheekplate opposite said cam, ring, said cheek plate and housing walls cooperating to,

provide. a pressure chamber, said restrictor passage interconnecting said pressure chamber and said groove where.- by pressure .in said chamber will.urge said last named face plate against said cam ring and said ,cam ring against said other face plate.

. References Cited in the file of this patent UNITED STATES PATENTS Ray July 15,

704,756 1902 1,988,875 Saborio Jan. 22, 1935 2,312,891 Ferris Mar. 2, 1943 2,544,987 Gardiner et al. -Q.-- Mar. 13, 1951 2,623,470 Hartmann Dec. 30, 1952 2,641,193 Klessig June-9, 1953 2,653,550 Gardiner et al Sept. 29, 1953 2,681,621 Hedman June 22, .1954 2,710,581 Rosaen June 14, 1955, 2,755,741 Erskine July 24, 1956 r 2,762,312 Adams et al. Sept. 11, 1956 2,787,224 Udale Apr. 2, 1957 2,809,588 Stewart Oct. 15, 1957 2,832,199

Adams et al. Apr. 29, 1958 

